Calculating machine



5 Sheets-Sheet 1 A TTORNEY Marh 12, .1935. Q M- F, FRlDEN CALCULATINGMACHINE Filed May 29, 1950 BMW March 12, 1935. c. M. F. FRIDEN 1,993,834

CALCULATING MACHINE Filed May 29, 19504 5 Sheets-Sheet 2 FIEJE- 505 507am V w32/ l Y f/ INVENTOR.' Ca// M E Haie/@f7 Bymfnag/ ATTORNEY March12, 1935. c. M. F. FRIDEN 1,993,834

CALCULATING MACHINE Filed May 29, 1950 3 Sheets-Sheet I5 FIE E-'ATTORNEY Patented Mar. 12, 1935 UNITED STATES CALCULATING MACHINE CarlM. F. Friden, Piedmont, Calif., assignor to Marchant Calculating MachineCompany, a corporation of California Application May 29, 1930, SerialNo. 456,843

1 Claim.

The present invention relates to calculating machines, and particularlyto the type embodying a rotary actuator drum into which the values to becalculated are set, and from which, upon rotation thereof, these valuesare transmitted to an accumulator register.

The invention is an improvement on that described in the patent toFriden No. 1,524,924, dated February 3, 1925, and is shown embodied in acalculating machine of the type described in the patent to Friden No.1,643,710, dated September 27, 1927 to which reference will herein be-rnade for the disclosure of a complete calculating machine includingmechanisms as are not specically described herein. Although theaccompanying drawings show the invention embodied in a machine of thegeneral type disclosed in the latter patent mentioned above, it ismanifest that the invention may be embodied in a calculating machinehaving any suitable means for differentially controlling the actuator,or any suitable form of accumulator register.

It is an object of the invention to provide an improved, simple, anddependable actuating mechanism for calculating machines.

Another object of the invention is the provision, in mechanism of theclass described, of means for eliminating or minimizing undesirableresults due to the relative movement of the driving and driven elementsat the time they are engaged.

` Another object of the invention is the provision of a structure of theclass described in which frictional resistance is minimized.

Another object of the invention is the provision of a structure of theclass described in which noise incident to the operation thereof isminimized.

Other objects will appear as the description progresses.

The invention possesses a plurality of advantageous features, some ofwhich will be set forth at length in the following description, wherethat form of the invention which has been selected for illustration inthe drawings accompanying and forming a part of the presentspecification will be described in full. In said drawings, one form ofapparatus embodying the invention has been shown, but it is to beunderstood that the invention has not been limited to such form, sincethe invention, as set forth in the claim, may be embodied in a pluralityof other forms.

In the accompanying drawings forming a part .of this specication:

Figure 1 is a longitudinally vertical section through a calculatingmachine showing one section of keys and the elements associatedtherewith for setting the value to be calculated into the rotatableactuator.

Figure 2 is a right side View of the differentially settable cam and itsassociated setting mechanism which is operated by any of a plurality ofkeys shown in Figure 1.

Figure 3 is a right side view of the differentially settable cam showingthe locking means provided therefor.

Figure 4 is a left side view of an actuator disc showing the pivotedgear segment and its associated roller which causes its substantiallyradial oscillation in respect to the actuator disc by operating in thegroove of the aforementioned cam.

Figure 5 is a section through the actuator disc, gear segment, andcamming mechanism in their juxtapositional relation on the actuatordrive shaft.

Figure 6 is a plan view of the pivoted gear segment and its associatedcam showing the plurality of settable positions of said cam and theresultant paths described by each of the gear segment teeth in respectto the operable tooth of its driven accumulator gear while said gearsegment is being oscillated radially on its own pivot by said cam, androtated about the axis of the actuator disc by the actuator drive shaft.

Selection mechanism The calculating machine shown in the accompanyingdrawings is of the keyboard type, in which the values selected areintroducedrinto the actuator1 by the depression of keys, as shown in thelatter mentioned patent. Obviously, however, the cam comprising `part ofthe present device can be differentially set by any suitable means.

The depression of a key introduces a value corresponding to the numeralon the key into a rotatable actuator, rotation of the actuator beingeffected to accomplish the calculating operation. The values introducedinto the actuator are transmitted, on rotation thereof, to the numeralwheels of the accumulator register, which, for the purpose of makingdirect action of the selected values on the numeral wheels of highestvalue possible, is disposed in parallel displaceable relation with thevalue selecting mechanism axis. As explained in the latter patentmentioned above, the leverage between the selecting bar 300 and itscomember 301 is such that a key of a small denomination depresses thebar 300 very slightly while each key of the next higher order adds tothe depressed distance of said bar, which motion is transmitted throughpin 3021 to bell crank 302, serving to rotate bell crank 302 in acounterclockwise direction about the axis 303. On the upper end of bellcrank 302, (Fig. 2) and concentric with the shaft 303, is a curved rack304 which meshes with the gear 305 secured to the differentiallysettable box cam 306. It is obvious that each increase ofcounter-clockwise rotation of the bell crank 302 is transmitted throughthe curved rack 304 and gear 305 serving to im- 'part in direct ratio alike increase of clockwise rotation to the box cam 306 about the axis ofthe shaft 307 and on the ball bearings 310 (Fig. 5) provided therefor.Obviously, the successive depressing of the keys 308 in the order oftheir increasing value from one to nine inclusive, will serve to rotatebox cam 306 in a clockwise direction to nine different positions inaddition to that normally occupied by it when no key is depressed. Meanshave been providedl for indicating the values which have been enteredinto the machine by the depression of the keys. Each selecting elementis provided with a dial 309 upon which the numerals from zero to nineare successively delineated, and the numeral representing the value ofthe key depressed is visible through an appropriately positionedaperture in the machine casing.

Selection lock and zero stop Means have been provided whereby the entireselecting mechanism is ,free while the machine is in neutral positionwith all setting and controlling means released. Means have also beenprovided whereby the selecting mechanism is locked in any one of aplurality of predetermined positions during one or more completerevolutions of the actuator. Means have also been provided whereby theselecting mechanism will be automatically returned to and held at zeroor neutral position upon the completion of one or more revolutions ofthe actuator and upon the release of all setting and operating means.

'Ihese operations are accomplished by the provision of a lockingmechanism comprising a plurality of vertical lock pawls 800, secured tothe shaft 802 which is suitably journaled at both ends. Secured to theshaft 307 is a cam 806 provided on its periphery with a depression 805into which the arm 804, alsointegral with shaft 802, is normally held bysuitable spring pressure. The rotation of the actuator shaft in eitherdirection will serve to throw the arm 804 out of its normal seat in thedepression 805 to the high portion of cam 806 which, in turn, serves torotate shaft 802 and its integral lock pawls 800 through a limited arcin a counter-clockwise direction. This rotation serves to force theprojection 801 of lock pawl 800 in any one of a pluralityof depressions311 in the periphery of box cam 306, dependent on the angulardisplacement from its normal position, thereby locking the entireselecting mechanism until a full revolution has been completed.

During the calculation of a problem in multiplication or division, it isnecessary that the selecting mechanism remain locked during a pluralityof revolutions of the actuator. Therefore, means vhave been provided toaccomplishlthis through an arm 803 integral with the shaft 802 (Fig. 1)which is so connected with the operating means of the machine that thelock pawls 800 are held in locking contact until any number ofrevolutions of the actuator has been completed, or until the operatingmeans have been released, as disclosed in the latter mentioned patent.

Means have been provided whereby the selecting mechanism isautomatically returned to and held at neutral or zero position at theend of a calculating operation and when all setting and operating meanshave been released. The bell crank 302 is provided with a projection 312opposite its fulcrum point from the operating pin 3021. Tensionedbetween this projection 312 and a. point on the machine base is a spring313 tending to rotate the rack 304 secured to bell crank 302 in aclockwise direction, which, in the absence of other instrumentalities,would be rotated out of mesh with gear 305. 'I'his has necessitated theprovision of a zero stop comprising, in the form illustrated, aprojection 314 on the periphery of the box cam 306 which rotates in acounterclockwise direction by virtue of the spring teny sion alreadyexplained, until it contacts and comes to rest against a face ofprojection 801 on lock pawl 800 (Fig. 3). Similarly, an overthrow stopis provided by the projection 315 on the periphery of box cam 306,which, when the nine key-is depressed, has an angular displacement ofsufficient magnitude to also engage a face of projection 801 on lockpawl 800, thereby preventing overthrow. Obviously, the box cam 306 isdiiferentially displaceable only through a limited arc, and is locked inany one of a plurality of positions while the shaft 307, rotates theactuator disc 316 and its co-member the pivoted gear segment 317, whichare juxtaposed with the box cam 306. The connecting mechanism and mode4of operation will be described as this specication progresses.

The pivoted segment Means are provided whereby any angular dis--placement of the box cam 306, the magnitude of which is determined bythe depression of a key representing the digit delineated thereon, will,

when the actuator is rotated, cause the said digit Y to be added intothe accumulator by rotation in one direction, or subtracted by rotationin the opposite direction. This is' accomplished by the provisionof anactuator disc 316, splined to the shaft 307 (Fig. 5), and upon which ismounted a nine tooth gear segment 317 (Figs. 4, 5, and 6) journaled on astud 318, and held thereon by any suitable means; in this case, theretainer ring 321. Secured to the segment 317 is a projecting stud 319which carries a roller 320. The relation of the gear segment 317 (Fig.5) with the box cam 306 is such that the roller 320 rotatably mounted onthe gear segment is confined in the box cam path 306 which has a lowportion 306A (Fig. 6), with relation toits axis of rotation 306C, and ahigh portion 306B. .That portion of the cam path from 306A to 306B in acounter-clockwise direction, has a veryv abrupt radial rise, and,conversely, that portion of the cam path from 306A to 306B in aclockwise direction, has a very gradual radial rise. Obviously, with thebox cam 306 locked in any of a plurality of stationary positions, andwith the actuator disc carrying the segment 317 around the cam with thesegment roller confined within the path of the box cam 306, the segment317, through the roller 320, will have, when rotated in acounterclockwise direction, imparted to it an abrupt ejectingoscillation about its pivot point 318 while the roller 320 travelsthrough the short portion of the cam between 306A and 306B, andI agradual retracting. oscillation through the long portion of the cambetween 306B and 306A. Likewise, a reverse movement is obtained when theactuator disc carries the gear segment in a clockwise direction'.

As previously stated in this specification, means have been providedwhereby any predetermined digit can be set into the actuating mechanismin such a manner that it is transferred to the accumulator register,either additively or subtractively, upon a revolution of the actuatormechanism. For illustrative purposes, a diagrammatic view (Fig. 6) hasbeen provided showing the resultant paths described by each of the Cilgear Asegment teeth with respect to the operable tooth of the drivenaccumulator gear 400 while said gear segment is being oscillatedradially o-n its own pivot by said cam, and rotated about the axis ofthe actuator discv by the actuator drive shaft. The positions numberedfrom zero to nine inclusively, denote the plurality of diierentiallysettable positions taken by the center angular displacement in theopposite direction.v

These positions are denoted by the gear teeth numbered from 1a to 9a,inclusively. Gear segment 317 is shown in its neutral or full cycleposition on one actuator disc, and is also shown out of its full cycleposition in the phantom line figure 317A (Fig. 6). In this latterposition, the roller 320 is at the low portion of the cam which placesthe gear segment in its extreme 'retracted position radially. Continuedrotation in a counter-clockwise direction will result in an abruptejection of the roller 320 and the segment 317 rotatable on 4its pivotvpoint 318 until the roller reaches the high portion of the cam 306B atwhich time the segment will have attained its extreme radial ejection.It is this abrupt counter-clockwise radial ejection, or conversely,clockwise radial retraction that must be so timed with respect to thegear 400 that any predetermined number of segment teeth will contact theteeth of the gear 400 and result in a like number of circular pitchdisplacements thereof, each displacement corresponding to a digit on theaccumulator numeral wheel.

In actuator mechanisms of this type heretofore, it has been necessary toemploy the most abrupt cam rise practicable so that the resultant curveof the segment teeth caused by their concurrent rotation and radialmovement would be on a sufficiently radial line to assure the propermeshingv of the segment teeth into the accumulator gear without thepossibility of an error. Due to the short leverage caused by theoperating roller of the segment being nearer to the pivot point than tothe segment teeth, the present invention overcomes these disadvantagesby causing the majority of the segment teeth to be ejected and retractedrapidly enough against the direction of rotation that the segment teethenter radially, or better. In the majority of the paths 1b to 9b (Fig.6), it is manifest that the rate of radial movement has been equal to orgreater than the rate of rotation even though a comparatively smoothcamming Iaction has been used. This more radial movement of the segmentteeth assures perfect mesh without Working to the close limitsheretofore necessary in the manufacture of this type of actuating drum,while the more smooth camming. action serves decidedly to decrease noiseas well as undue strain on the drive mechanism of the machine ingeneral.

The relative positon of the tooth a on the gear 40o with the @am drop ois such that rotation of the actuator in a counter-clockwise directionwill eject the segment after all teeth have passed the gear 400, androtation in a clockwise direction will retract the segment before anytooth can mesh with the gear 400, thus being inoperative in eitherdirection, or zero position with no key depressed.

If the number one key were depressed, the abrupt rise in the cam wouldbe angularly displaced from zero to one position, but for illustrativepurposes, the cam will be left in zero position and the operable toothof the gear 400 will be given a like angular displacement in theopposite direction or position la. Obviously, counter-clockwise rotationof the actuator will now result in a continuous retracted position ofthe segment until eight teeth have passed the tooth la of gear 400 whenthe roller 320 strikes the abrupt rise in the cam 306, causing the ninthtooth of the segment to describe path 1b which serves t-o rotate thegear 400 a distance of one circular pitch. Rotation of the actuator inthe opposite direction results in the segments meshing with the gearwhile fully ejected, only to be retracted radially after only one toothhas operated the gear 400.

If the number nine key were depressed, the abrupt cam rise would beangularly displaced from zero to nine position, or, leaving the cam atzero, the gear 400 would be relatively displaced to position 9a. Acounter-clockwise rotation will now serve to eject all of the segmentteeth along their respective paths 1b to 9b, immediately before meshingwith the gear 400 which ejection will be continued until each of thenine teeth has displaced a corresponding tooth of the gear a distance ofone circular pitch, thus transmitting nine to the accumulator. Aclockwise rotation will result in the segments meshing the gear 9a fullyejected only to be abruptly retracted after each of the nine teeth ofthe segment has performed its operation. Thus, it is obvious how theoperation of transmitting any predetermined numeral from the actuator tothe accumulator can be followed through by placing the gear in any ofits relative positions from 0a to 9a.

Means have been provided whereby a tens transfer is eiected to thenumeral wheel of the next higher order at the necessary time by theprovision of tens carrying pin 322 (Fig. 1) transversely displaceableinto operative position by the transfer levers 403 which levers arerestored to inoperative position by the cam 323 secured to the oppositeside of the actuator disk from the segment. Tens transfer mechanism ofthis type are Wellknown in the art of calculating machines, so need nofurther explanation.

Means have also been provided whereby no two of a plurality of theactuator segments placed in axial alinement and composing the actuatordrum assembly, can engage the accumulator gears simultaneously, thussuddenly applying a large load to the driving mechanism. This has beenaccomplished by angularly displacing the neutral position of each gearsegment from every other.

I claim:

In a calculating machine, the combination of accumulating mechanismcomprising a toothed Wheel, differential actuating means thereforcomprising an adjustable selecting cam, a member rotatable with respectto said cam having an actuating rack pivoted thereto by a pivot arm ofxed length, and means connecting said rack with said cam for oscillatingsaid rack in the plane of said wheel by moving it about said pivot assaid member is rotated.

CARL M. F. FRIDEN.

